EP1576629B1 - Device for production of an electrical energy storage device comprising an improved rolling spool - Google Patents

Description

The present invention relates to the field of electrical energy storage assemblies.

More specifically, the present invention relates in particular to multi-layer electrochemical assemblies based on polymeric materials comprising an electrolyte flanked by two electrodes respectively forming cathode and anode.

The invention applies in particular, but not exclusively, to devices comprising a lithium-based anode.

The present invention applies to the realization of capacitors, super-capacitors and generators or batteries.

Examples of such electrochemical assemblies can be found in the documents FR-A-2737339 , FR-A-2759087 , FR-A-2759211 , FR-A-2808622 .

The present invention relates to a device for the realization, automatically and continuously, such electrical energy storage assemblies, in the form of generally flat slabs, to allow easy stacking and connection in serial / parallel form , of several such sets.

The inventors have found that it is particularly advantageous to make such electrical energy storage assemblies in the form of a generally planar multi-layer winding from the beginning, in order to avoid the occurrence of folds or equivalent defects in the structure of said sets.

Indeed, the inventors have found that the realization of such sets in the form of a circular winding revolution, subsequently flattened, frequently leads to defects such as folds or bumps in the different layers, and a bad interface between them, where appropriate a local detachment between the different layers resulting in a weakening of the storage capacity, in because of the stresses generated in the turns which have a developed different from one turn to the other.

The inventors have also found that these problems, related to the state of the art, can accelerate the aging of the elements, by reducing the number of charge / discharge cycles tolerated by the elements, in the case of batteries, or even up to self-discharge of the elements.

More precisely, in this context, the purpose of the present invention is to propose a device for manufacturing multi-layer assemblies with an electrical energy storage function having qualities superior to the prior art.

This object is achieved in the context of the present invention by means of a device for producing electrical energy storage assemblies comprising a mandrel adapted to wind up superposed films in the form of a multi-layer assembly, characterized in that the cross-section of the mandrel has a general spindle cross-section and comprises means capable of modifying the straight section of the mandrel on command, the section modification of the mandrel comprising a reduction in the length of the long axis of the mandrel.

As will be explained hereinafter, the section modification of the mandrel can in particular be used to pinch one end of the films to be wound, the origin of the winding and / or to cause a general loosening of the winding relative to to the mandrel, ie to create a certain clearance between the winding and the outer surface of the mandrel, in order to facilitate the extraction of the winding.

The present invention also relates to a method for producing electrical energy storage assemblies by winding superposed films, on a mandrel, in the form of a multi-layer assembly, characterized in that it comprises at least one step of modifying on command the cross section of the mandrel, having a general spindle section, by reducing the length of the major axis of the mandrel.

• la figure 1 représente une vue générale schématique des moyens principaux composant le dispositif conforme à la présente invention,
• la figure 2 représente une vue en bout partielle à échelle agrandie d'un mandrin d'enroulement conforme à un mode de réalisation préférentiel de la présente invention,
• la figure 3 représente une vue schématique des moyens d'enroulement conformes à la présente invention, composés de la combinaison d'un tel mandrin d'enroulement et d'un rouleau presseur associé,
• les figures 4, 5 et 6 représentent des vues similaires des moyens d'enroulement dans trois positions successives de leur cinématique,
• la figure 7 représente une vue partielle de moyens conformes à la présente invention situés en amont d'un ensemble de complexage,
• la figure 8 représente une vue partielle similaire de moyens conformes à la présente invention situés en aval de cet ensemble de complexage et en amont d'un module d'enroulement,
• les figures 9 à 16, qui seront décrites plus en détail par la suite, illustrent schématiquement, en coupe transversale, les structures multi-couches mises en oeuvre à différents stades de l'alimentation du dispositif conforme à la présente invention,
• les figures 17 à 20, qui seront également décrites plus en détail par la suite, représentent des vues en coupe transversale des trois structures multi-couches de base utilisées dans le cadre de l'invention et de la structure multi-couche résultante, avant pelliculage, destinée à l'alimentation du mandrin, les figures 17 à 20 illustrant plus précisément le positionnement relatif des bords latéraux longitudinaux des différentes couches impliquées,
• la figure 21 représente schématiquement un enroulement conforme à la présente invention (la figure 21 représente un nombre de spires inférieur à la réalité pour simplifier l'illustration),
• la figure 22 représente schématiquement des moyens d'entraînement d'un mandrin d'enroulement et d'un rouleau presseur associé, conformes à la présente invention,
• la figure 23 représente schématiquement des moyens de coupe localisée d'un collecteur de courant,
• la figure 24 représente schématiquement le collecteur de courant résultant comportant des coupes localisées,
• la figure 25 représente schématiquement un enroulement comportant de telles coupes,
• la figure 26 représente schématiquement le déploiement d'un collecteur de courant obtenu grâce à de telles coupes,
• la figure 27 représente les courbes d'évolution de vitesse du mandrin d'enroulement conforme à la présente invention et d'un rouleau presseur associé, à l'origine de l'enroulement, pour une rotation complète sur 360°, en fonction de leur position angulaire,
• la figure 28 représente des courbes similaires de variation de vitesse du mandrin et du rouleau presseur à la fin d'un enroulement, en fonction de leur position angulaire,
• la figure 29 représente la variation du rayon d'enroulement en fonction de l'angle du mandrin ainsi qu'une courbe de variation d'un facteur de correction en fonction de cet angle,
• la figure 30 représente un tableau qui illustre les données utilisées pour piloter l'évolution de la vitesse de rotation du mandrin d'enroulement,
• la figure 31 représente une vue schématique du bord tranchant d'une lame de coupe conforme à un mode de réalisation préférentiel de la présente invention,
• la figure 32 représente schématiquement un mode de réalisation préférentiel d'un dépelliculeur conforme à la présente invention,
• la figure 33 représente un synoptique général du dispositif conforme à la présente invention.
• la figure 34 représente une vue en coupe horizontale, selon le plan de coupe référencé XXXIV-XXXIV sur la figure 8, de moyens de commande de mors du mandrin,
• la figure 35 représente, en position juxtaposée deux demi-axes de commande de déplacement relatif des mors du mandrin,
• la figure 36 représente une vue en coupe transversale d'un tronçon de l'un de ces deux demi-axes, selon un plan de coupe référencé XXXVI-XXXVI sur la figure 38,
• la figure 37 représente une vue axiale en bout des deux demi-axes précités,
• les figures 38 et 39 représentent des vues respectives latérales des deux demi-axes,
• la figure 40 représente une vue en plan, selon une vue orthogonale aux figures 38 et 39, d'un tel demi-axe,
• la figure 41 représente une vue latérale des moyens mécaniques de commande des demi-axes assurant l'orientation relative des deux mors du mandrin,
• la figure 42 représente une vue selon l'orientation référencée XXXXII sur la figure 41 des mêmes moyens,
• la figure 43 représente une vue partielle des mêmes moyens, notamment des vérins de commande, selon l'orientation référencée XXXXIII sur la figure 41,
• les figures 44A à 44F représentent six positions successives des mors du mandrin au cours d'une séquence de fermeture du mandrin,
• la figure 45 représente les mors du mandrin en position initiale pour la rotation du mandrin en vue d'un enroulement,
• les figures 46A à 46H représentent huit positions successives des mors du mandrin au cours de cette rotation,
• les figures 47A à 47F représentent six positions successives du mandrin et d'un rouleau presseur additionnel escamotable au cours de la séquence du dernier tour d'enroulement,
• la figure 48 schématise la phase d'escamotage de ce rouleau presseur additionnel,
• la figure 49 schématise la phase d'arrêt de rotation du mandrin et d'ouverture des mors,
• la figure 50 schématise la phase d'extraction de l'élément enroulé,
• les figures 51A à 51E schématisent cinq positions successives et relatives des portes mors du mandrin,
• les figures 52A à 52E représentent respectivement les cinq positions des mors du mandrin correspondant respectivement aux figures 51A à 51E,
• les figures 53A à 53E représentent les cinq positions de moyens de commande mécanique correspondant respectivement aux cinq figures 51A à 51E,
• la figure 54 représente une variante de réalisation du mandrin,
• les figures 55A et 55B représentent deux vues d'une autre variante de réalisation du mandrin, respectivement dans une position de préhension de bande par aspiration d'air et d'extraction d'élément,
• les figures 56A, 56B et 56C représentent trois vues d'une autre variante de réalisation de mandrin, respectivement en position d'enroulement, en position d'extraction, et en vue axiale,
• la figure 57 représente une vue schématique en bout d'un mandrin conforme à une autre variante de réalisation,
• la figure 58 représente une vue en bout d'un mandrin conforme à une autre variante de réalisation selon l'invention, et
• la figure 59 représente une vue schématique en bout d'un mandrin conforme à une autre variante de réalisation de l'invention.

Other features, objects and advantages of the present invention will appear on reading the detailed description which follows and with reference to the appended drawings given by way of non-limiting examples and in which:

• the figure 1 represents a schematic overview of the main means constituting the device according to the present invention,
• the figure 2 represents an enlarged partial end view of a winding mandrel according to a preferred embodiment of the present invention,
• the figure 3 is a schematic view of the winding means according to the present invention, composed of the combination of such a winding mandrel and an associated pressure roller,
• the Figures 4, 5 and 6 represent similar views of the winding means in three successive positions of their kinematics,
• the figure 7 represents a partial view of means according to the present invention situated upstream of a complexing assembly,
• the figure 8 represents a similar partial view of means according to the present invention located downstream of this complexing assembly and upstream of a winding module,
• the Figures 9 to 16 , which will be described in more detail below, schematically illustrate, in cross-section, the multi-layer structures implemented at different stages of the supply of the device according to the present invention,
• the Figures 17 to 20 , which will also be described in more detail below, represent cross-sectional views of the three basic multilayer structures used in the context of the invention and the resulting multi-layer structure, prior to film coating, intended for the feeding of the mandrel, Figures 17 to 20 illustrating more precisely the relative positioning of the longitudinal lateral edges of the various layers involved,
• the figure 21 schematically represents a winding according to the present invention (the figure 21 represents a number of turns less than reality to simplify the illustration),
• the figure 22 schematically shows drive means of a winding mandrel and an associated pressure roller, according to the present invention,
• the figure 23 schematically represents localized cutting means of a current collector,
• the figure 24 schematically represents the resulting current collector including localized sections,
• the figure 25 schematically represents a winding comprising such sections,
• the figure 26 schematically represents the deployment of a current collector obtained by means of such sections,
• the figure 27 represents the speed evolution curves of the winding mandrel according to the present invention and of an associated pressure roller, at the origin of the winding, for a complete 360 ° rotation, as a function of their angular position,
• the figure 28 represents similar curves of speed variation of the mandrel and the pressure roller at the end of a winding, as a function of their angular position,
• the figure 29 represents the variation of the winding radius as a function of the mandrel angle as well as a curve of variation of a correction factor as a function of this angle,
• the figure 30 represents a table which illustrates the data used to control the change in the speed of rotation of the winding mandrel,
• the figure 31 is a schematic view of the cutting edge of a cutting blade according to a preferred embodiment of the present invention,
• the figure 32 schematically represents a preferred embodiment of a depelliculator according to the present invention,
• the figure 33 represents a general block diagram of the device according to the present invention.
• the figure 34 represents a horizontal sectional view, according to the section plane referenced XXXIV-XXXIV on the figure 8 , jaw control means of the mandrel,
• the figure 35 represents, in juxtaposed position, two half-axes for controlling relative movement of the jaws of the mandrel,
• the figure 36 represents a cross-sectional view of a section of one of these two half-axes, according to a sectional plane referenced XXXVI-XXXVI on the figure 38 ,
• the figure 37 represents an end axial view of the two aforementioned half-axes,
• the Figures 38 and 39 represent respective lateral views of the two half-axes,
• the figure 40 represents a plan view, according to a view orthogonal to Figures 38 and 39 , of such a half-axis,
• the figure 41 represents a side view of the mechanical control means of the half-axes ensuring the relative orientation of the two jaws of the mandrel,
• the figure 42 represents a view according to the orientation referenced XXXXII on the figure 41 the same means,
• the figure 43 represents a partial view of the same means, in particular control cylinders, according to the orientation referenced XXXXIII on the figure 41 ,
• the Figures 44A to 44F represent six successive positions of the chuck jaws during a chuck closing sequence,
• the figure 45 represents the jaws of the mandrel in initial position for the rotation of the mandrel for winding,
• the Figures 46A to 46H represent eight successive positions of the jaws of the mandrel during this rotation,
• the Figures 47A to 47F represent six successive positions of the mandrel and an additional retractable pressure roller during the sequence of the last winding turn,
• the figure 48 schematizes the retraction phase of this additional pressure roller,
• the figure 49 schematizes the stop phase of rotation of the mandrel and opening of the jaws,
• the figure 50 schematizes the extraction phase of the wound element,
• the FIGS. 51A to 51E schematize five successive and relative positions of the chuck jaws,
• the Figures 52A to 52E respectively represent the five positions of the jaws of the mandrel corresponding respectively to the FIGS. 51A to 51E ,
• the Figures 53A to 53E represent the five positions of mechanical control means respectively corresponding to the five FIGS. 51A to 51E ,
• the figure 54 represents an embodiment variant of the mandrel,
• the Figures 55A and 55B represent two views of another embodiment of the mandrel, respectively in a strip gripping position by air suction and element extraction,
• the Figures 56A, 56B and 56C represent three views of another embodiment of mandrel, respectively in the winding position, in the extraction position, and in axial view,
• the figure 57 represents a schematic end view of a mandrel according to another embodiment variant,
• the figure 58 represents an end view of a mandrel according to another embodiment of the invention, and
• the figure 59 is a schematic end view of a mandrel according to another embodiment of the invention.

In the remainder of the description, the terms "upstream" and "downstream" will be used with reference to the direction of movement of the complexes in the device, the term "upstream" qualifying the elements situated before a given reference, while the term "downstream" qualifies the elements located after this one.

• des moyens A d'alimentation en structures multi-couches, et
• des moyens E d'enroulement de ces structures.

The device for producing electrical energy storage assemblies according to the present invention essentially comprises, as illustrated in FIG. figure 1 annexed:

• means A for supplying multi-layer structures, and
• E means of winding these structures.

The supply means A have the function of conveying several single-layer or multi-layer assemblies 90, 92, 94, initially separated, and of complexing, that is to say superimposing and binding, these. The power supply means A also have the function of ensuring precise relative positioning of the longitudinal edges of the various layers involved in the final complex 96.

The various single-layer or multi-layer elements and the resulting complexes implemented in the context of the present invention are moved parallel to a frame 900 whose function will be defined in more detail later.

The particular embodiment of the device illustrated on the figure 1 annexed is intended for the realization of generating sets formed of a stack of six layers: a collector 10 (for example of aluminum), a cathode 20 (for example based on POE (polyoxyethylene) and lithium salt), a an electrolyte layer 30, an anode 40, for example lithium, an electrolyte layer 50 and a cathode 60. The electrolytes 30 and 50 are for example based on LiV ₃ O ₈ or V ₂ O ₅ and POE. The Al collector 10 is preferably coated with an anticorrosion barrier, for example based on Ti nitride or the like, for example graphite.

However, the invention is not limited to this particular example.

In this context, the supply means A comprises three separate feed magazines 100, 200 and 300.

The feed means 100 is intended for supplying a four-layer complex 90 comprising the above-mentioned cathode 60 and electrolyte layer 50 sandwiched between two external protective films 80, 81 (see FIG. figure 9 ).

The feed means 200 is for feeding the anode sheet 40 (see figure 11 ).

The feed means 300 is for supplying a five-layer complex 92 comprising: the electrolyte 30, the cathode 20 and the collector 10 sandwiched between two outer protective films 82, 83 (see FIG. figure 13 ).

Preferably, each of these supply means 100, 200, 300 comprises a coil of the desired complex, 90, 40 or 92, previously made by any appropriate means, rotatably placed on the common frame 900 about respective axes of rotation. 102, 202, 302.

Of course, the coils forming the feed magazines 100, 200 and 300 are removably mounted on the frame 900 to be replaced after exhaustion.

The complexing of the three sets 90, 40 and 92 respectively from the three supply means 100, 200 and 300, that is to say the stacking of these sets, is performed in a complexing module C interposed between the output supply means 100, 200, 300, and the winding means E.

On the figure 1 the coils of the complexes 90, 40 and 92 placed in the three feed means 100, 200, 300 are respectively referenced 104, 204, 304.

The four-layer complex 90 coming from the coil 104 is guided towards the complexing module C by rollers 110, 112, 114.

Downstream of the coil output 104, the module 100 includes a dewatering assembly 120 designed to remove the face-side film 81 to be complexed on the electrolyte 50. This depelliculating assembly 120 is positioned between the return rollers 112 and 114.

The three-layer complex structure 50, 60, 80 obtained at the outlet of the depelliculating assembly 120 is illustrated on the figure 10 .

Furthermore, the feed means 100 comprises between the depelliculating assembly 120 and the complexing module C a heating module 130. The structure and function thereof will be described in more detail later.

Similarly, the five-layer complex 92 coming from the coil 304 is guided towards the complexing module C by rollers 310, 312, 314.

Downstream of the coil outlet 304, the module 300 includes a dewatering assembly 320 designed to remove the face-on film 82 to be complexed on the electrolyte 30. This dewatering assembly 320 is positioned between the return rollers 312 and 314.

The four-layer complex structure 83, 10, 20, 30 obtained at the outlet of the depelliculating assembly 320 is illustrated in FIG. figure 14 .

Furthermore, the supply means 300 comprises between the depelliculating unit 320 and the complexing module C a heating module 330. The structure and function thereof will be described in more detail below.

The feed assembly 200 for feeding an anode film, preferably lithium-based, comprises two feed rollers 240, 250 of respective films 84, 85.

The films 84, 85 and the anode film 40 are guided by rollers 210, 212 towards a primary application assembly 260. The function of this assembly 260 is to combine in the form of an element comprising the anode layer. 40 sandwiched between the two films 84, 85, these initially separate films from the respective feed coils 204, 240 and 250.

The element comprising the two films 84 and 85 surrounding the anode 40 is illustrated on the figure 12 .

The applicator assembly 260 is preferably formed of two nip rollers 262, 264 rotatably mounted about respective parallel axes, receiving the three aforesaid films 84, 40, 85 with each other. Preferably, one 262 rollers has its axis of rotation fixed in space, while the second roller 264 placed opposite, which serves as a pressure roller, is urged to move against the roller 262 first mentioned, under a controlled effort, for example by means of elastic means, such as an elastic blade 263.

Moreover, at least one of the two rollers 262, 264 is motorized. It is controlled to alternately pull the element 84, 40, 85, and brake this element in synchronization with the downstream process. As such the rollers 262, 264 are slaved slave on the downstream process means.

Where appropriate at least one of the rollers 262, 264 is mounted on a retractable crew, for example driven by a jack, to allow separation of the two rollers 262, 264 and thus facilitate the initial establishment of the element 84 , 40, 85 between them.

Downstream of the application assembly 260, the supply means 200 comprises a transverse sectioning module 270 of the anode layer 40.

To this end, the sectioning module 270 comprises a hammer system 272 and anvil 274 respectively disposed on either side of the path of movement of the element 84, 40, 85. The hammer 272 operates by transverse linear striking through protective films 84, 85.

At least one of the hammer 272 or the anvil 274, preferably the hammer 272, comprises a blunt edge.

The hammer 272 is biased sequentially to the striking against the anvil 274 to define in the anode initial film 40, a downstream length corresponding to the desired winding. It will be noted that the hammer 272 operates on the element comprising the anode 40 sandwiched between the two films 84, 85. However, the films 84, 85 are formed of a material capable of withstanding the striking of the hammer 272 to avoid any breakage of the films 84, 85.

The two films 84, 85 are removed from the aforementioned element illustrated on the figure 12 , at the output of the sectioning module 270 by means of depelliculation 220, 225. Where appropriate these means of Dehulling 220, 225 may be formed by the hammer 272 and the anvil 274 themselves.

The section of the anode 40 situated in front of the break line defined by the module 270 is driven by the downstream drive means, this anode section 40 being itself sandwiched between the two assemblies 50. , 60, 80, on the one hand, and 83, 10, 20, 30, on the other hand, in the complexing module C.

The section of the anode film 40 located upstream of the rupture line is in turn driven by the films 84, 85, since these, as indicated previously, are not sectioned in the module 270.

It should be noted on this point that the set of films 80, 81, 82, 83, 84 and 85, has not only the function of avoiding pollution of the external faces of the complex by the external environment and of preventing the sticking of complex on the different rollers involved, but also participates in the training of their associated complex.

The films 80, 81, 82, 83, 84 and 85 are advantageously based on PP (polypropylene), PE (polyethylene), PET (polyethylene terephthalate) or the like.

When they are removed, they are removed as far as possible in their path, so that the associated film never goes naked on a roller of its path, to avoid pollution of both the film and the roller.

Note also that the two film unwinders 240, 250 associated with the anode unwinder 204 are substantially adjacent and that the film 84 from the unwinder 240 surrounds the anode roll 204 on a winding arc ("docking" according to the expression dedicated) important (typically greater than 90 ° and preferably at least equal to 270 °) to both ensure good protection of this fragile film and ensure adequate mechanical drive. This winding arc of the anode 204 by the film 84 is referenced β on the figure 7 attached. It varies according to the radius of the external turn of film present on the unwinder 240.

The sequential control on the one hand, the driving of the films 84 and 85, and consequently of the anode section 40 located upstream of the rupture line, and on the other hand, the driving of the films 80 and 83 and therefore the anode section located downstream of this break line, is preferably adapted to define a gap, for example of the order of 20mm between the two aforementioned sections, after rupture. More precisely, the striking of the tool 272 is synchronized with the braking stop of the nip rollers 262, 264 so as to create a running interruption of the lithium 40 while the lamination continues downstream at the same speed.

This prevents, thanks to the pre-breaking of the anode layer 40, having to cut downstream, simultaneously, all the layers composing the final complex, which could pinch all the layers together and could lead to short circuits between the anode 40, the cathodes 20, 60 and the collector 10.

To avoid damaging the interface adjacent to the films, in particular by tearing, when removing them, preferably the skinning, at the positions 120, 220, 225 and 320 above, is achieved using a scraper system 230 schematized on the figure 32 , arranged tangentially to the film concerned and having a polished edge 232 almost sharp, adapted to ensure peeling of the film through a sharp deviation thereof of at least 60 ° (see figure 32 ), if appropriate with turning on itself thereof substantially 180 °, according to a small radius of curvature (typically a radius close to 0.05mm). The scraper 230 is formed of a static blade blunt ridge 232 near the plane of displacement, upstream, of the film which carries the film. The edge 232 has its convexity directed downstream of the displacement of the film. The inventors have indeed determined that such a peel makes it possible to preserve the surface of the adjacent complex, whereas a tearing of the film without precaution generally deteriorates that -this. The above-mentioned scraper 230 makes it possible peeling of the film by shearing between the functional film and the protective film. By pulling the protective film around the edge 232 of the wiper 230, an elongation of the outer curvature of the protective film layer is created, which locally creates a tangential force on said layer, a micro-stretching of the film and a sliding effect of the film layer on the functional film, thus avoiding the tearing of particles of the functional product.

Preferably, the device also comprises means for adjusting the tensile force exerted on the protective film when it is deflected on the blunt edge 232 of the scraper 230.

On the figure 1 , the scraper system of the depelliculating assemblies 120, 320, are referenced 122, 322. The films 81, 82, 84 and 85, removed on the stations 120, 320, 220 and 225, are directed towards respective rolls 124, 324, 224 and 229. For this purpose, the films 84 and 85 are guided by rollers 221, 222, on the one hand, and 226 on the other hand.

The heating means 130 and 330 have the function of bringing to controlled temperature the external interface surface of the electrolytes 50 and 30 before they are brought into contact with the anode layer 40 in the complexing assembly C , to allow a good adhesion thereafter between the electrolyte layers 50 and 30 and the anode 40. Preferably, these heating means 130 and 330 are formed by ovens with rapid temperature rise and rapid temperature reduction, capable of operating a hot air sweep, by forced circulating loop and regulated hot air, on the aforementioned interfaces. Typically, the heating means 130 and 330 are designed to dispense thermostatic compressed air, at the accuracy of ° C, for example at 60 ° C, on the electrolyte interfaces 50 and 30.

More precisely still, the assembly of the device according to the present invention comprising sequential phases of displacement interruption of the feed films upstream of the winding module E, to allow the cutting of the complex, the evacuation successive of each winding, and the reengagement of a next element, preferably the ovens 130 and 330 are also controlled sequentially. That is to say that the diffusion of hot air, in the ovens 130 and 330 is interrupted cyclically when stopping the scrolling of the complexes, in order to avoid a harmful rise in temperature of the portion of the complexes located in these ovens. An overexposure to heat of these sections of films could indeed alter the quality of the final complex.

Moreover, in order to avoid an unwanted rise in the temperature of stagnant film sections in the furnaces, during the stopping phases, the heating means 130, 330 may comprise means capable of sequentially blowing a jet of fresh compressed air onto the films . These means are typically adapted to reduce the temperature inside the furnaces to a value of the order of 40 ° C.

Preferably ovens 130, 330 are formed of a loop circuit. In the figures there is referenced 132, 332, the sections of these furnaces in which the multilayer films circulate and 134, 334 fans sequentially ensuring the blower of hot air and cold air. To provide heating, preferably heating elements consisting of bare electrically conductive multifilaments are placed opposite the output of the fans 134, 334.

We spotted on the figure 1 IX, X, XI, XII, XIII, XIV, XV and XVI, respectively, the localization on the path of the device of the various complexes illustrated in FIGS. Figures 9, 10, 11, 12, 13, 14, 15 and 16 .

It is important to control the relative positioning of the longitudinal side edges of the various films 10, 20, 30, 40, 50 and 60 forming the complex from the set C, in order to avoid parasitic electrical contacts between these different layers.

We have shown on the figure 17 the relative positioning of the longitudinal edges of the film 80, the cathode 60 and the electrolyte 50 downstream of the screening station 120. It will be noted that the cathode 60 has a width less than the electrolyte 50, that this the last overflows on both sides of the cathode 60, the film 80 has a width greater than the electrolyte 50 and it overflows on both sides thereof.

We have shown on the figure 18 , the relative positioning of the longitudinal edges of the films 84, 85, and the anode 40. It will be noted that the anode 40 has a width less than the two films 84, 85, which may have identical widths and that the films 84, 85, overflow on both sides of the anode 40.

We have shown on the figure 19 , the relative positioning of the film 83, the collector 10, the cathode 20 and the electrolyte 30. It will be noted that the cathode 20 has a width less than the collector 10, a first edge of the cathode 20 is flush with a first edge of the collector 10, that the electrolyte 30 has a width greater than the cathode 20, that it overflows on either side thereof, that the electrolyte 30 overflows with respect to the first edge of the cathode 20 and of the collector 10, but that the second edge of the electrolyte 30 is set back from the collector 10, the film 83 has a first edge which protrudes with respect to the first edge of the electrolyte 30 but has a second edge which is flush with the second edge of the electrolyte 30.

Finally, we have shown on the figure 20 , the relative positioning of the film 80, the cathode 60 of the electrolyte 50, the anode 40, the electrolyte 30, the cathode 20, the collector 10 and the film 83, at the output of the module complexing C.

It should be noted that the edges of the electrolytes 50 and 30 are superimposed, the anode 40 having a recessed edge of the electrolytes 50 and 30 on the emerging side of the collector 10, while the anode 40 passes electrolytes 30, 50 on the side opposite.

XVII, XVIII, XIX and XX were referenced on the figure 1 , the location of the complexes represented respectively on the Figures 17, 18, 19 and 20 .

The relative positioning of the layers represented on the Figures 17 and 18 is ensured during the realization of the supply coils 104 and 304. The relative positioning shown on the figure 19 is assured during filming in the module 260. The relative positioning shown in FIG. figure 20 is ensured in the complexing module C.

In order to define the relative positioning (which can also be called "relative alignment") required between the two subsets represented on the Figures 17 and 19 and the anode layer 40, preferably means are provided for detecting the positioning of the longitudinal edges of the respective complexes upstream of the complexing assembly C and means able to move these complexes, with respect to a common reference system , upstream of the complexing module C, to obtain the desired relative positioning. Preferably, these displacement means act on the feed means 100, 200 and 300. For this purpose, preferably, each of these feed means 100, 200 and 300 is mounted on an individual plate capable of controlled movement by relative to the general support frame 900 of the device. More precisely, preferably, each of these plates is pivotally mounted about a respective axis 101, 201, 301 and associated with a controlled displacement means.

The means for detecting the positioning of the edges of the complexes are preferably formed by optical means, optionally infrared or laser, or ultrasonic means, arranged on a fork with two transmitter / receiver elements respectively arranged on either side the travel path of the multilayer.

On the figure 1 such detection means associated with the complex coming from the means 100, 280 have been referenced the equivalent means of detection associated with the complex coming from the means 260 and 340 the equivalent means of detection associated with the complex coming from the means 300. The detection means 140 is placed between the roller 114 and the oven 130. The detection means 340 is placed between the roller 314 and the oven 330. The detection means 280 is placed between the primary complexing module 260 and the complexing module C.

The aforementioned displacement means may be formed of means based on pneumatic cylinders or any equivalent means.

Preferably, each of the aforementioned plates carries a damping means adapted to rest against the aforementioned common frame 900 to prevent vibration of the device. By way of non-limiting example, these damping means may be formed of suction cups.

The aforementioned pivot axes 101, 201 and 301 are preferably parallel to the plate 900. They pass through the center (axis of rotation 102, 202, 302) of the unwinders 104, 204, 304 and by a median plane of the width of the reel placed on the unwinder. They are also parallel to the associated respective multilayer film sections located immediately upstream of the complexing complex C, imposed by the rollers 114, 262 and 314.

In this respect, it will be noted that the section of the anode film 40 situated upstream of the complexing module C, guided by the roller 262, is situated substantially along the bisector of the angle formed by the sections of the complexes 90 and 92 respectively unwinders 104 and 304, upstream of the complexing module, as guided by the rollers 114 and 314. More precisely still, upstream of the complexing module, the complexes 90 and 92 form an angle of about 150 ° between them and the anode film 40, located along their bisector is substantially 75 ° from each of these two complexes 90 and 92.

Similarly, preferably, the anode 40 is located, upstream of the complexing module C, substantially along the bisector of the sections of the films 84 and 85 located downstream of the depelliculeurs 220 and 225, which sections of films 84 and 85 are made between them. an angle of the order of 60 °.

The return rollers 110, 112, 114, 221, 222, 226, 310, 312 and 314 make it possible to arrange the loaders 104, 204 and 304 in remote positions, and to bring together the complex sections involved, upstream of the module. complexing C so that the complete angle formed between them, at the level of the complexing module, is less than 180 °.

It will be noted that the aforementioned relative positioning means of the base complexes not only have the function of guaranteeing a satisfactory electrical connection in the final product, and in particular protection of the cathodes by overflow of the electrolyte, to avoid short circuits, but also to optimize the active surface in operation, in the smallest possible complex width.

The receiving rollers of the different depelliculating assemblies 124, 224, 229, 324, 520 and 522 preferably comprise motorized reels.

Similarly, the unwinders 104, 204 and 304 are preferably motorized and parameterized to control the tensile force, constant on the multilayer films involved. It is indeed important to maintain constant traction on the films to have a reproducibility in the realization of the elements.

The motors thus associated with the unwinders 104, 204 and 304 are alternately controlled as a motor, at the origin of a complex winding, and then as a brake when the drive of the complex is supported by downstream means.

It will be noted in particular that in this context, the motors of the various unwinders 104, 204, 304 and skin cleaners 124, 224, 229, 324, 520 and 522 are controlled by a central unit programmed to suitably change the motor forces and the respective braking forces required by taking into account the evolution of the diameter of rolled films and respectively the rolled film diameter.

These diameters can be either calculated by the central unit, from the respective length of complex and treated film, or measured using appropriate sensors, for example ultrasound, respectively equipping each of the unwinders and reels concerned 104, 204, 304, 124, 224, 229, 324, 520 and 522.

The complexing unit C preferably comprises two pinch rollers 400, 410, rotatably mounted about parallel axes and between which is conveyed the stack formed of the superimposed layers: film 80, cathode 60, electrolyte 50, anode 40, electrolyte 30, cathode 20, collector 10 and film 83.

The two pinch rollers 400, 410 are biased in relative proximity under a controlled effort. They therefore exert a controlled pressure force on the films conveyed between these rollers 400, 410. For this purpose, preferably, the axis of rotation of the roller 400 is fixed while the axis of rotation of the roller 410 is mounted on a roller. crew urged to move towards the roller 400 above under a controlled effort, for example by an elastic member such as a blade 412. Preferably the roller 410 is also mounted on a retractable crew driven by a drive means, for example a cylinder, to ensure the release of the roller 410 on command and facilitate the establishment of the complex.

Thus, at the output of the complexing assembly C, the stack illustrated on the figures 15 and 20 .

If appropriate, the laminating rollers 400, 410 may be heating. Their diameter is typically at least 20 mm.

The device according to the present invention further comprises, between the complexing module C and the winding module E, a set 500 with multiple functions and having in particular the function 1) of controlling the flow (length) of complex, in a module 510, 2) to perform localized longitudinal sections in the manifold 10, at a module 520, 3) to alternately ensure the drive of the complex at the beginning of a winding and the braking of this complex when it is placed in tension by the mandrel 610, at a module 530, 4) to remove the films 80 and 83, in a module 540, 5) to cut the layers 10 to 60 of the functional stack after scrolling. a length corresponding to the desired winding, in a module 550 and 6) to heat the outer faces of the resulting stack at the end of a winding, at a module 560.

The detection device 510 is intended to control a correction of the synchronization defects that may result from micrograding of the complex on the rollers 400, 410, in order to ensure a constant feeding speed of the winder E.

By way of nonlimiting example, such a detection device 510 may be formed of a synchronization roller 512 mounted on a pivoting lever 514 and biased against the moving complex by a pneumatic cylinder or any equivalent means, and associated to an absolute encoder 516.

The complex is pressed against the roller 512 by a roller 518 placed upstream on the path of displacement of the complex.

The cutting module 520 is intended to perform a linear sequential slitting, in the longitudinal direction, on the edge of the collector 10. In the accompanying figures the resulting section sections are referenced 521. Each section 521 has a substantially equal length L1, while being slightly lower, at a half winding circumference on the mandrel 610. The actuation of this device 520 is controlled so that the slits 521 are found all superimposed on the same face of the final wound element. In other words, these slits 521 are operated with a pitch P1 identical to the length of each turn made on the mandrel 610. Insofar as this length is variable and increasing, because of the thickness accumulated on the mandrel 610, preferably the pitch of slits 521 is also variable.

As schematically illustrated on the figure 26 annexed, at the final conformation station 700, a transverse cutting segment 522 is operated between an axial end of the above-mentioned cut-out 521 and the adjacent free edge of the collector 10, and the external lateral strip 523 thus delimited in the collector 10 is extended to the outside of the wound element, to serve as a connector on the current concentrator. On the figure 26 the collector band portion 10 thus deployed is referenced 525.

The slitting device 520 is preferably of the "air-cut" type. It comprises an oscillating slitting blade 524 adapted to cut locally and sequentially the collector 10, between two rollers 526 and 528 serving to support the complex. On the figure 23 the pivoting movement of the blade 524 is shown schematically as 529.

The drive module 530 preferably comprises two pinch rollers 532, 534, between which the complex assembly illustrated in FIGS. figures 15 and 20 . These two rollers 532, 534 are associated with respective engines. When routing the front end of the complex to the mandrel 610, the rollers 532, 534 are driven in drive motor mode. On the other hand, once the front end of the complex gripped by the mandrel 610, the latter becomes a motor, and the rollers 532, 534 are driven, by their respective motor, in the braking mode. This ensures a narrow veneer of the complex on the mandrel 610. These two nip rollers 532, 534 are located near the winding mandrel 610, upstream thereof.

The drive of the nip rollers 400, 410 is slaved to that of the nip rollers 532, 534 which operate as master, with respect to the slave rollers 400, 410.

At least one of the rollers 532, 534 is associated with a biasing means such that the rollers 532 and 534 exert on the complex that they frame, a controlled clamping force.

Furthermore, preferably at least one of the rollers 532, 534, for example the roll 534, is mounted on a retractable crew 535, for example driven by a jack 536, to facilitate the insertion of the complex between the rollers 532 and 534.

The removal of the films 80 and 83 is carried out in the module 540 using scrapers 541, 543 similar to the scrapers 122 and 322 mentioned above. The films 80 and 83 are directed, after skinning, by means of rollers 542, 544 on accumulation rollers 546, 548. These are motorized, as indicated above.

The complete transverse sectioning of the stack of the resulting 6 layers 10, 20, 30, 40, 50 and 60 of the complex is operated, just downstream of the depelliculating blades 541, 543, in the module 550, by any appropriate means.

Preferably these cutting means 550 comprise a blade 552 comprising a cutting edge 554 formed of a convex dihedral to two symmetrical slopes (see figure 31 ) animated with a fast speed of displacement, under short run when the cut is required.

The movements of the cutting blade 552 are controlled by a means 556 preferably formed of a jack. Furthermore, the cutting blade 552 is preferably placed on a retractable crew driven by a specific displacement means, for example a second jack 558, to allow the blade to be retracted on demand, in order to facilitate the installation of the blade. complex, or any other required maintenance intervention.

Alternatively these cutting means may be formed of a hammer / anvil system similar to that previously described under references 272, 274.

The cut made by the cutting means 552 is operated substantially in the middle of the gap formed in the lithium anode layer 40, at the striking station 572/574. So as we see on the figure 21 the anode layer 40 is set back from the other layers composing the winding, both at the front end and the rear end of the winding.

Moreover, as we see on the figure 21 preferably the two axial ends Ei, Ee of the finished winding In are not superimposed. In other words, the outer end Ee of the winding is interrupted below the internal end Ei, to avoid an extra thickness at this level. Thus, the flattened finished winding generally has an identical thickness over its entire extent.

The heating of the external faces of the stack is operated by any appropriate means in the module 560, for example by blowing hot air pulsed or passing on a heating roller.

This heating is preferably provided by a retractable hot air blowing bar 562 located immediately downstream of the cutting device 550, for heating a transverse band of the complex, in order to prepare the heat-sealing of the end of the winding.

We will now describe the winding means E according to the invention.

These mainly comprise a mandrel 610 rotatably mounted about an axis 611.

The mandrel 610 has a cross section, transverse to its axis of rotation 611, non-circular of revolution. The mandrel 610 is substantially flat. It has a general section in a spindle. Typically the ratio between a major axis and a minor axis of its cross section is greater than 3, preferably greater than 5 and very advantageously greater than 10. It advantageously has a generally elliptical cross section.

More specifically, the outer casing of the mandrel 610 is preferably delimited by two sectors of convex revolution cylinder having identical radii (R1 on the figure 2 ), but distant parallel axes; moreover this outer envelope delimiting the cross section of the mandrel has blunt ends 615, 616 with a small radius.

The mandrel 610 has a length (considered parallel to its axis of rotation 611) greater than the width of the complexes to be wound.

More precisely still, preferably, the mandrel 610 is formed of two jaws 612, 614, symmetrical and complementary. The interface between the two jaws 612, 614, that is to say the mutual bearing surface between them, in the winding position, referenced 613 in the figures is preferably flat and connects the two curved surfaces convex outer shell of the mandrel away from the tapered ends of the outer shell ellipse.

By way of nonlimiting example, the major axis of the mandrel 610, formed by the two jaws 612 and 614 contiguous, is of the order of 12 cm while the small axis of the mandrel 610, formed by the two jaws 612 and 614 contiguous, is of the order of 9 to 10 mm, the angle formed between the oblique plane which corresponds to the interface 613 between the two jaws 612, 614 and the major axis of the spindle is typically of the order of 2, 5 °, the spindle is terminated, on the ends 615, 616 of the major axis, by arcs of the order of 0,15mm of radius, and the distance separating them centers of the cylindrical main surfaces of the mandrel is greater than 6 times their radius R1.

The two jaws 612, 614 are associated with drive means, for example hydraulic jacks or the like adapted to provide controlled controlled relative movement of the two jaws between a first position in which the two jaws 612, 614 are spaced apart. to allow the insertion of the front end of a complex stack 10 to 60 to be wound and a second position in which the two jaws 612, 614 are joined to allow the winding of the aforementioned complex stack.

The mandrel 610 formed by the cooperation of the two jaws 612, 614, is itself driven to rotate about its axis 611, at a non-constant speed, according to terms to be defined later.

The mandrel 610 is associated with a pressure roller 620.

It is rotatably mounted about its axis 622 on the end of a rotating arm 624.

The arm 624 is rotated about an axis 625 eccentric with respect to the axis 622, and at a speed twice that of the mandrel 610, so that the roll 620 rolls successively on each of the faces of the mandrel 610, more precisely on the complex stack 10 to 60 wound on it, in order to press it regularly and prevent any formation of folds in the stack. The arm 624 is preferably rotated mechanically by the rotation of the mandrel 610 with a multiplier ratio of 2.

Chuck 610 and arm 624 rotate in the same direction of rotation.

The displacement kinematics of the mandrel 610 and the roll 620 are schematized on the Figures 3 to 6 associated.

By way of non-limiting example, as illustrated on the figure 22 , the mandrel 610 and the arm 624 can be driven by a common belt 640 associated with a motor 642, by means of respective rollers 618, 628 engaged with said common belt 640. to provide a double speed to the arm 624, the roller 628 associated therewith has a drive ratio two times lower than the roller 618 associated with the mandrel 610, is typically a circumferential dimension two times smaller.

Note that the device preferably further comprises a roller 570, downstream of the cutting blade 552, facing the hot air blowing nozzle 562.

This roll 570 serves as the ultimate guide to the formed complex, before winding on the mandrel 610.

The generatrix of the roll 570 on which the complex is based is situated in a plane defined by the generatrix of the upstream roll 534 and the generatrix of the mandrel 610 corresponding to the minor axis thereof (which generator serves as a support for the complex when it is positioned with its major axis parallel to the aforementioned plane, as illustrated on the figure 5 ).

The assembly formed by the combination of the mandrel 610, the arm 624 and the pressure roller 622 is mounted on a drawer 630 itself associated with drive means adapted to move the assembly in translation between a winding position such that illustrated on the figure 1 , closer to the module 500 and an evacuation position, remote from these means 500, once the desired stacking length wound on the mandrel 610, to facilitate removal of the winding obtained.

The aforementioned drawer 630 can also be moved to a temporary additional initial position, close to the supply pinch rollers 532, 534, when these are driven in motor, to ensure the gripping of the front end of the complex at the beginning of the 'winding. Once this seizure is made, preferably the drawer 630 is spaced from the nip rollers 532, 534 for the actual winding.

To complete the winding and to avoid a floating of the outer rear end of the wound complex, the mandrel 610 is preferably driven in a complete rotational movement over 360 ° after breaking the wound complex and complete winding of this complex and the pressure roller 620 is held in support on the winding during this additional rotation to complete the "gluing" of the last turn of the winding, thanks to the aforementioned preheating by the means 560. If necessary, this heating can be completed by a hot air blowing at the winding station E.

This results in a bonding of the tail of the winding, without adding glue.

Note that the device may further comprise, as illustrated in FIG. figure 8 , an additional retractable pressing roller 580, placed between the roller 570 and the mandrel 610. Such a roll 580 has the function of allowing the blocking of the complex during cutting and the plating of the end of the strip, on the mandrel 610. The roller 580 is preferably connected, by an elastic blade 582, to an oscillating assembly 584, driven by a jack 586.

During the winding of the complex winding, on the mandrel 610, the roller 580 is placed in the position illustrated on FIG. figure 8 , spaced apart from the path of displacement of the complex and remote from the mandrel 610. At the end of a winding, after cutting the complex, on the contrary, the aforementioned oscillating equipment and the associated roller 580 are moved so that the roller 580 is plated on the face of the mandrel 610 opposite to that on which the roller 620 rests.

This winding, obtained in a generally flattened form, thanks to the elliptical geometry of the mandrel 610 is then removed from the mandrel 610 and discharged by a robot or any equivalent means adapted to a pressing station 700 intended to perfect the flatness of each winding obtained .

Such a robot may be formed of a pneumatic robot with clamping grippers for gripping the wound element for storing electrical energy on the mandrel 610, its extraction thereof and by various movements of rotations and translations, placing the element in the pressing station 700.

Essentially this pressing station comprises a press, formed for example of a pressing cylinder 710, responsible for final flattening of the element. This operates preferably in masked time, while a next element is being wound up.

To facilitate removal of the winding obtained, the device may comprise means capable of ensuring during a limited sequence, at the end of the winding, a relative and reciprocating displacement in translation between the two jaws 612 and 614 constituting the mandrel 610. , in a direction parallel to the interface 613, to thereby vary the length of the major axis of the mandrel, in order to slightly "loosen" the winding relative to the mandrel 610, take off the first turn and peel the attachment of the first round .

Each winding can then be directed to a magazine for performing subsequent steps required for connection under the desired serial / parallel configuration. Such a store and the means used to provide the required serial / parallel links, will not be described in more detail later.

As previously indicated, according to an advantageous characteristic of the invention, the mandrel 610 is rotated at a non-constant angular velocity controlled so that the linear speed of travel of the complex stack feeding the chuck 610 is constant.

Thanks to this characteristic, the invention makes it possible to guarantee a constant tensile force on the complex and consequently a perfect winding on mandrel 610, free of any fold or equivalent defect.

Moreover, thanks to the constant speed of scrolling of the complex, it avoids any need to have an intermediate store, upstream of the winding module E, to absorb the acceleration-deceleration jolts of the band. And it allows the realization of the entire device in compact form, in a limited volume.

We have illustrated in strong lines on the figure 27 , the speed variation curve of the mandrel 610 at the origin of the winding.

On the same figure 27 the speed variation curve of the arm 624 carrying the pressing roller 620 is illustrated in fine lines.

Note that are illustrated under the abscissa axis of the figure 27 the relative positions of mandrel 610 and pressure roller 620.

More precisely still, the angular rotation speed of the mandrel 610 is corrected during the winding, to take account of the evolution of the winding radius resulting from the variation of complex thickness accumulated on the mandrel 610 in order to guarantee the linear speed constancy of scrolling.

We have thus illustrated on the figure 28 in strong lines the speed variation curve of the mandrel 610 packed with a thickness of 5.5 mm of complex (corresponding for example to 19 turns of winding) and in fine lines the corresponding curve of variation of the speed of the roll 620.

On the figures 27 and 28 the angular ranges in which the pressure roller 620 bears on the mandrel 610 are marked below the abscissa axis under the reference PA.

It will be noted in the examination of figures 27 and 28 , that the speed of rotation of the mandrel 610 and the crew 624 carrying the pressure roller 620, is high when the winding of the complex is operated on a small radius (ie a winding radius of the order size of the small axis of the mandrel 610), or when the mandrel 610 is oriented substantially parallel to the conveyed complex section. Then this speed drops when the winding radius grows (and approaches the long axis of the mandrel 610), that is to say when the mandrel 610 is oriented substantially perpendicularly to the conveyed complex section.

Thus the speed of rotation of mandrel 610 and pressure roller 620 has a cyclical evolution: 2 peaks per rotation of 360 °. This evolution is inversely proportional to the evolution of the winding radius.

Furthermore, it will be noted that the pressure roller 620 comes into contact with, and remains in contact with, the complex film wound on the mandrel 610 when it is driven in rotation at low speed. This arrangement ensures a good contact between the pressure roller 620 and the wound film and therefore between the different layers of the wound film.

The figure 28 which corresponds to the end of a winding has a range of speed evolution less extensive. Indeed, because of the complex thickness accumulated on the mandrel 610, the winding radius ratio covers a smaller range than at the origin of the winding.

Thus during the winding of an element, the speed of rotation varies at each turn over a period of 180 °. Moreover, the winding time per revolution increases because the winding length on the mandrel 610 increases from one revolution to another due to the thickness added to the mandrel 610.

As a result, speeds and accelerations gradually decrease during winding.

We also see on the figure 29 on the one hand, a smoothed curve V1 of variation of the winding radius as a function of the angular position of the mandrel and, on the other hand, a smoothed curve V2 of variation of a correction factor as a function of this angular position. .

The abscissa has an angle range of 0 to 180 °. This also covers the range from 180 to 360 °, the aforementioned curves having a periodicity of 180 °. In addition, the ordinate scales were used, the amplitude of the winding radius was recorded on the left, and the amplitude of the correction factor on the right.

The inventors have in fact determined that the correction factor to be applied to the basic evolution V1 of the angular rotation speed taking into account only the evolution of the naked winding radius as a function of the angular position of the mandrel, to take into account of the variation in thickness of the winding could be likened to such a smoothed curve V2 which varies as a function of the angular position of the mandrel 610, while being fixed for a given angle regardless of the number of turns previously wound on the mandrel .

We illustrated on the figure 30 a table schematizing an example of data used in the context of the present invention to control the driving motor of the mandrel 610.

We find on the first two columns of the table of the figure 30 , the rotation angle of the mandrel.

These two columns respectively correspond to the ranges of 0 to 180 ° and 180 to 360 °, because of the symmetry existing between the two successive half turns of the same winding turn. Indeed a complete turn is wound after a rotation of 360 °. Thus we find the same thickness on both sides of the mandrel during the two half-periods of successive 0 to 180 ° and 180 to 360 ° winding of the same turn.

The third column of the figure 30 represents the radius of the mandrel 610 bare, ie at the origin of the winding.

The fourth column of the figure 30 represents the correction factor shown on the figure 29 .

The pairs of columns that follow on the figure 30 represent two by two, for each winding tower, one the winding radius, and the other the speed of rotation of the mandrel 610.

dans laquelle :

• ro représente le rayon du mandrin (610) nu,
• F représente le facteur de correction mentionné dans la quatrième colonne,
• n représente le rang de la spire en cours, ie le nombre d'enroulements opéré sur le mandrin 610 et
• e représente l'épaisseur du complexe enroulé sur le mandrin 610.

More specifically, as shown in the table of the figure 30 for each winding turn, the winding radius r is calculated on the basis of the relation: $$\mathrm{r}=\mathrm{ro}+\left(\mathrm{F}\mathrm{.}\mathrm{not}\mathrm{.}\mathrm{e}\right)$$

in which :

• ro represents the radius of the mandrel (610),
• F represents the correction factor mentioned in the fourth column,
• n represents the rank of the current turn, ie the number of windings operated on the mandrel 610 and
• e represents the thickness of the complex wound on mandrel 610.

dans laquelle :

• V représente la vitesse linéaire constante recherchée pour le complexe, et
• r représente le rayon d'enroulement précédemment calculé.

Then the speed of rotation of mandrel 610 is calculated on the basis of the relation: $$\mathrm{\omega }=\mathrm{V}/\left(\mathrm{2.}\mathrm{\Pi }\mathrm{.}\mathrm{r}\right)$$

in which :

• V represents the constant linear velocity sought for the complex, and
• r represents the previously calculated winding radius.

In practice, control of the driving motor of the mandrel 610 can be operated, either using precalculated data and stored in adapted memories, or using data calculated directly by a central unit on the base, on the one hand, the law of evolution of the winding radius as a function of the geometry of the mandrel 610 and, on the other hand, of the correction law depending on the evolution of this radius as a function of the thickness of the winding previously made on the mandrel.

The aforementioned data are applied successively to each angular fraction of the rotation of the mandrel 610, on the drive motor thereof.

By way of nonlimiting example, for a linear speed of the order of 6 m / min, the mandrel 610 reaches a speed of the order of 180 rpm, ie an angular speed of the order of 1090 ° / s, hence a sampling rate of the order of 1 ° / ms.

The choice to work closer to the degree requires a refreshing of the motor speed setpoint close to the ms.

In this context, the speed setpoint intended to be applied to the motor is selected of a digital nature, to avoid the processing of analog / digital converters.

Obviously, a control module ensures the complete enslavement of all the means involved in the realization of the winding of the complex.

The various aforementioned axes including the axes 102, 202, 302, rollers 104, 204, 304, the axis 611 of rotation of the mandrel 610, the axis of rotation of the pressure roller 620 and the pivot axis of the oscillating arm 624 , the axes of the rollers 124, 224, 240, 250, 229, 320, 520 and 522 associated with the films, the axes of the return rollers 110, 112, 114, 221, 222, 210, 212, 226, 310, 312, 314 and the axes of the pressure rollers 262, 264, 400, 410 are parallel to each other and preferably horizontal.

According to another advantageous characteristic of the invention, the device comprises a housing divided into two compartments separated by a vertical partition 900: a first compartment, in a controlled dry atmosphere which houses all the means 100, 200, 300, 400, 500 , 600 and 700 above and a second compartment which houses the control means and drive / motor associated. The aforementioned vertical partition wall constitutes the support frame of the various axes of rotation described above.

If necessary, an additional sweep of dry air may be provided in the operational chamber.

The present invention typically allows the realization of a complex winding comprising between 16 and 19 turns, corresponding to a complex length of the order of 4 to 5.5m, ie a total winding thickness of about 5 , 5 mm. The running speed of the complex is typically between 2 and 10 m / min. It is advantageously of the order of 6m / mm.

By way of nonlimiting example, the device according to the present invention is suitable for treating widths of complex of width between 50 and 150 mm.

The present invention offers many advantages over the means proposed in the state of the art.

• le fait que la forme quasi plate du mandrin d'enroulement 610 évite de générer les contraintes rencontrées avec l'état de la technique, lors de la mise à plat,
• le réchauffage des complexes dans des fours et le complexage des multicouches formant cathode et collecteur sur le lithium, permettant de réaliser un collage de bonne qualité sans reprise intermédiaire des produits en optimisant le contact surfacique des couches entre elles, ceci améliorant les échanges ioniques entre les différentes couches fonctionnelles du produit final,
• le fait que toutes les fonctions du dispositif sont pilotées en automatique avec des paramétrages et des régulations précises de chaque fonction, ce qui permet d'assurer la reproductibilité avec un niveau de qualité toujours contrôlé.

In a nonlimiting manner, mention may be made of:

• the fact that the almost flat shape of the winding mandrel 610 avoids generating the stresses encountered with the state of the art, when laying flat,
• the heating of the complexes in furnaces and the complexing of the multilayers forming cathode and collector on the lithium, making it possible to achieve a good quality bonding without intermediate recovery of the products by optimizing the surface contact between the layers, this improving the ionic exchanges between the different functional layers of the final product,
• the fact that all the functions of the device are controlled automatically with precise settings and regulations of each function, which ensures reproducibility with a level of quality always controlled.

It will be remembered that, in general, all the rollers and rollers or unwinders used in the device of the invention have alternately motor and / or brake functions, depending on the sequence of the winding involved, to guarantee traction. constant on all films, complexes and associated films.

As stated previously, the figure 33 represents a general synoptic of the main means of the device according to the present invention.

As indicated above, the device according to the present invention comprises mechanical means capable of modifying the straight section of the mandrel 610 to order.

The section modification of the mandrel 610 can in particular be used to pinch one end of the films to be wound up, at the origin of the winding and / or to cause a general loosening of the winding, ie to create a certain clearance between the winding and the outer surface of the mandrel 610, to facilitate the extraction of the winding. This latter function can be obtained for example by controlled reduction in the length of the long axis of the mandrel 610.

We will now more particularly describe the specific means of the present invention, adapted to change on command the cross section of the mandrel 610 when it is formed of two complementary jaws 612, 614.

The aforementioned means are designed to ensure on command a relative displacement of the two jaws 612, 614, relative to each other, according to at least one component transverse to the axis of rotation 611 of the mandrel 610.

Each jaw 612, 614 is attached to a respective jaw holder 652, 654. Each of these jaws is rigidly connected to a shaft 653, 655 rotatably mounted on a mandrel body 660 about respective off-center axes 656, 657. relative to the axis of rotation 611 of the mandrel 610, but parallel thereto. More precisely, the shafts 653 and 655 are rotatably mounted on a plate 661 belonging to the mandrel body 660.

Those skilled in the art will understand that the rotation of a shaft 653, 655, and therefore of the jaw holder 652, 654, and associated jaw 612, 614, respectively, relative to the mandrel body 660, causes a displacement of bit involved in relation to each other.

For this purpose each shaft 653, 655 carries a pinion 658, 659 with helical cut. By way of non-limiting example, the size angle of the gears 658, 659 may be of the order of 17 °.

The pinions 658, 659 linked to the jaw holders 652, 654 are angularly driven by two respective control half-axes 670, 680.

These can be the subject of various embodiments.

They are preferably in accordance with Figures 35 to 40 .

On these two half-axes 670, 680 can be seen generally symmetrical with respect to a longitudinal axial plane passing through their common axis of rotation, which coincides with the axis 611 of rotation of the mandrel 610.

The half-shafts 670, 680 are juxtaposed and arranged in a sheath 662 linked to the mandrel body 660. They are designed to be moved in translation, parallel to their axis, by means which will be described later.

The sheath 662 serves as a rocket providing rotational guidance of the chuck body 660 about the axis 611.

Each half-axis 670, 680 comprises, at one end, a section cut into a helical gear 672, 682 conjugating with the pinions 658,659.

Furthermore each half-axis 670, 680 comprises a section 674, 684 of non-circular section of revolution, for example dihedron (the two dihedrums contiguous 674, 684 respectively belonging to the two half-axes 670, 680 forming in combination, a square ), disposed in a section of complementary section of the sheath 662. The engagement thus defined prohibits any relative rotation between the half-shafts 670, 680 and the sheath 662, but allows and ensures a relative axial guidance therebetween.

At their second end, the half-shafts 670, 680 are each provided with an enlarged head 676, 686, in the form of a half-crown. It will be seen later that each of these heads 676, 686 preferably carries means for adjusting elastic members biasing the half-axes to a rest position. To this end, each head has several housings 679, 689, for example 3 per head, equidistributed angularly.

Furthermore, each half-axis 670, 680 further comprises, on the one hand on the side of the head 676, 686 located towards the pinion 672, 682, a cylindrical section of revolution 675, 685 which serves as translation guide and on the opposite side of the head 676, 686, a shank 677, 687 projecting beyond the head 676, 686.

The two half-shafts 670, 680 are capable of relatively relative displacement relative to one another, to allow a relative inclination of the jaws 612, 614. For this purpose preferably sliding shoes are interposed between the two half-axes 670, 680, in lights 671, 673 provided for this purpose at the half-axis interface 670, 680.

The tails 677, 687 of the half-shafts 670, 680 are selectively biased into several positions chosen by mechanical means 800 which will be described later with regard to figures 41 , 42 , 43 and 53 .

Note that each of the two jaw holders 652, 654 can be moved independently of the other. It is the same for the two half-axes 670, 680, independent of each other to allow a desynchronization of movements between the two jaws 612, 614. This desynchronization is necessary in particular to pinch / imprison the new end of a band at the origin of a winding.

The rocket constituted by the aforementioned sleeve 662 is rotatably mounted on a bearing 634 connected to the slide 630 and equipped with two ball bearings 635, 636. The rocket 662 is provided, at its rear end opposite the mandrel 610, pinion 618 ( illustrated figure 22 ) cooperating with the toothed drive belt 640.

The pinion 618 comprises cells 619 in number identical to the number of housings 679, 689 formed in the heads 676, 686 of the half-shafts 670, 680.

In the case of non-limiting case, it is thus provided six cells 619 respectively aligned on the housing 679, 689.

Each housing 619 houses a compression spring 690. The springs 690 are thus interposed between the pinion 618 and the heads 676, 686 of the half-shafts 670, 680. The springs 690 therefore urge the half-shafts 670, 680 away from the In other words, the springs 690 automatically urge the jaws 612, 614 to close. Mechanical means 800 which will be described in more detail below with respect to the jaws 612, 614. Figures 41 to 43 and 53 have an inverse effect on the half-axes 670, 680. These mechanical control means 800, during their activation, in fact solicit the half-axes 670, 680 to the jaw holders 652, 654.

The force exerted by the springs 690 can be adjusted by screws 692 engaged in housings 679, 689 of the heads 676, 686. The adjustment of the screws 692 therefore makes it possible to adjust the clamping force exerted by the jaws 612, 614.

We find on the figure 34 , the pressure roller 620 mounted free of rotation via internal rolling means, about its axis 622 on an arm or base 624. Preferably, as seen on the figure 34 , the means ensuring the rotation of the pressure roller 620 about its axis 622 are formed of an articulated hub 623 adapted to allow self-positioning of the roller 620 clean to ensure a narrow plating thereof on the outer surface of the winding. In practice, the hinged hub 623 may consist of two low-distance bearings positioned at the center (considered in the longitudinal direction) of the roll 620 and allowing a certain angular displacement of the roll 620.

The arm 624 is itself rotatably mounted about an axis 625 'parallel to the aforementioned axis 622 and eccentric with respect thereto. More specifically, the arm 624 is rotatably mounted about the axis 625 'on a member 693. The latter forms a small carriage movable relative to the main slide or carriage 630 to compensate for the thickness variations of the winding, on mandrel 610, between the first and last turns.

Various means may be provided for driving the arm 624 to rotate about the axis 625 '. It is recalled here that the arm 624 is preferably driven at a rotation speed twice that of the mandrel 610.

According to the particular and nonlimiting embodiment shown in the accompanying figures, the arm 624 is integral with a shaft 694 centered on the axis 625 'and rotatably mounted on the small carriage 693 above.

A second shaft 695 carrying the pinion 628 designed to cooperate with the drive belt 640 shown in FIG. figure 22 is rotatably mounted about the axis 625 on a spacer connected to the drawer 630.

Furthermore, a homokinetic coupling 696 is interposed between the output of the drive shaft 695 and the input of the driven shaft 694 itself linked to the arm 624.

The homokinetic coupling 696 has the function of allowing a relative displacement of the shaft 694, parallel to itself, with respect to the shaft 695, during the increase in thickness of the the winding on the mandrel 610, while ensuring permanently a precise connection to rotation between the driving shaft 695 and the driven shaft 694.

The displacement of the small carriage 693 with respect to the main spool 630 is controlled by any appropriate means, preferably by a jack 644. The body of the jack 644 is hinged at 645 on the spool 630. Its spindle 646 is articulated on a first end of the spool. 647. The second end of the connecting rod 647 is hinged to the carriage 693. Finally, the connecting rod 647 is articulated, in its middle, on a rod 648 rotatably mounted elsewhere on the slide 630.

Thus, the pressure roller 620 is placed on the element wound on the mandrel 610 by the cooperation of the small carriage 693 and the cylinder 644. By way of non-limiting example, the travel path of the small carriage 693 relative to the 630, and therefore relative to the axis 611 of rotation of the mandrel 610, during the displacement of the roll on the wound film, may be of the order of 3 mm for the first turn and of the order of 8, 5mm on the completed element. The race differential between the original position of the naked mandrel and the finished element position is thus compensated for by the translation travel of the jack 644 and the small carriage 693.

Typically, but by way of nonlimiting example, the homokinetic coupling 696 is designed to allow a radial offset of the order of 25 mm between the parallel axes 625 and 625 'of the shafts 695 and 694, to enable the useful stroke to be carried out radial movement of the pressing roll 620 to the mandrel 610.

In summary, the pinion 628 transmits the rotary motion to the driven shaft 694 via the constant velocity coupling 696. The shaft 694 transmits its movement to the arm 624 which itself carries the central bearing of the satellite roller 620. The bearing of this roller is equipped with a pawl system about the axis 622 to allow self-alignment of the roller 620 against the turns during winding.

Furthermore, the satellite pressure roller 620 is carried by the small carriage 693 embedded on the drawer 630 of the mandrel. Due to the ratio ½ between the gears 628 and 618, the arm 624 and the pressure roller 620 which accompanies it rotate twice as fast as the mandrel 610, which allows the pressure roller 620 to press the winding at each half-turn of the mandrel.

The approach movement and spacing of the satellite roller 620 relative to the mandrel 610 is carried out using the connecting rod or lever 647 square and pneumatic jack 644 double effect.

• le tiroir 630 est susceptible de déplacement à translation horizontale par rapport au bâti de la machine et au rouleau 570 entre une position rapprochée du rouleau 570 pour saisir le début d'un enroulement et une position éloignée de celui-ci pour assurer l'enroulement. Le tiroir porte le corps de mandrin 660, le mandrin 610, les demi-axes 670, 680, le rouleau presseur 620 et les moyens qui lui sont liés.
• plus précisément, le rouleau presseur 620 est monté par l'intermédiaire du bras rotatif 624 sur un chariot 693, lui-même susceptible de translation par rapport au tiroir 630.
• le corps de mandrin 660 supporte les porte-mandrins 652, 654 qui supportent eux-mêmes les mors 612, 614. Le corps de mandrin 660 est monté à rotation autour de l'axe 611 sur le tiroir 630 et entraîné par le pignon 618.
• les porte-mors 652, 654, et par conséquent les mors 612, 614 eux-mêmes qui leur sont liés, sont montés à rotation autour d'axes respectifs 656, 657 sur le corps 660.
• enfin, les demi-axes 670, 680 sont montés à translation dans le corps 660. La translation de chaque demi-axe 670, 680 par rapport au corps de mandrin 660 entraîne, grâce à la coopération définie entre les filets hélicoïdaux prévus sur les pignons 658, 659 d'une part, 672, 682 d'autre part, la rotation des porte-mors 652, 654, et par conséquent des mors 670, 680 qui leur sont liés par rapport au corps de mandrin 660 et donc un déplacement des mors 612, 614 l'un par rapport à l'autre.

Synthetic :

• the slide 630 is movable in horizontal translation relative to the machine frame and the roller 570 between a position close to the roller 570 to capture the beginning of a winding and a position remote from it to ensure the winding. The drawer carries the mandrel body 660, the mandrel 610, the half-axes 670, 680, the pressure roller 620 and the means connected thereto.
• more specifically, the pressure roller 620 is mounted via the rotary arm 624 on a carriage 693, itself capable of translation relative to the slide 630.
• the mandrel body 660 supports the mandrel holders 652, 654 which themselves support the jaws 612, 614. The mandrel body 660 is rotatably mounted about the spindle 611 on the spool 630 and driven by the pinion 618.
• the jaw holders 652, 654, and therefore the jaws 612, 614 themselves which are connected thereto, are rotatably mounted about respective axes 656, 657 on the body 660.
• finally, the half-shafts 670, 680 are mounted in translation in the body 660. The translation of each half-axis 670, 680 relative to the mandrel body 660 drives, thanks to the cooperation defined between the helical threads provided on the pinions 658, 659 on the one hand, 672, 682 on the other hand, the rotation of the jaw holders 652, 654, and consequently the jaws 670, 680 which are connected to them relative to the mandrel body 660 and therefore a displacement of jaws 612, 614 relative to each other.

We will now describe the structure of the mechanical control means 800 illustrated on the figures 41 , 42 , 43 and 53 , designed to provide controlled movement of half-shafts 670, 680.

The means 800 have the function of defining several precise relative positions of the half-axes 670, 680 and consequently the jaws 612, 614.

Preferably, the means 800 are provided to ensure four precise relative positions of work jaws 612, 614, in addition to a rest position. These various positions and the means used to obtain them will be described later with regard to figures 51 , 52 and 53 .

More specifically, the mechanical control means 800 are designed to individually control each half-axis 670, 680 and therefore each jaw 612, 614.

The mechanical means 800 are preferably adapted to control sequentially, or a relative inclination between the two jaws 612, 614, for example to ensure opening and closing during the capture and release of the winding, a displacement relative relative to each other of the two jaws 612, 614, to change the length of the major axis and the short axis of the mandrel ("to give the belly to the mandrel"), in a final sequence of extraction of the winding.

To control a relative inclination between the two jaws 612, 614, the control means 800 are designed to operate a translational relative displacement between the two half-axes 670, 680.

Various means can be provided for this purpose.

In the context of the preferred embodiment of the invention, the two half-shafts 670, 680 have different lengths, more specifically the tails 677, 687 respectively of the two half-shafts 670, 680 which emerge on the back of the heads. 676, 686 preferably have different lengths as seen on the figure 35 .

Those skilled in the art will understand that the biasing of the tail 677 of greater length of the half-axis 670, without intervening on the half-axis 680 causes a rotation of only the jaw holder 652 and therefore the single jaw 612 by 660. Such a solicitation may be be operated using a cylinder 810, whose rod 812 is placed opposite the half-axis 670.

On the contrary to ensure a relative movement of the two jaws 612, 614 while maintaining a parallel position therebetween, the mechanical control means 800 must move the half-axes 670, 680 on identical strokes.

Various means can be provided for this purpose.

According to the embodiment shown in the accompanying figures, the means 800 comprise for this purpose a rocker 820 or articulated pusher rotatably mounted on the spool 630 about an axis 822. The rocker 820 is itself solicited by three levers 830 , 840,850 articulated on the slide 630 about an axis parallel to the axis 822 and preferably coincides with it. Each lever 830, 840, 850 is itself biased, via a clevis type connection 832, 842, 852 by the rod of a jack 834, 844, 854 respectively associated.

Springs urge the levers 830, 840, 850 to a rest position in which the rocker 820 is without action on the half-axes 870, 880. On the contrary, the cylinders 834, 844, 854 request the levers 830, 840, 850 in the direction of a closer of the rocker arm 820 to the half-axes 870, 880. The rocker arm 820 is itself capable of deflection relative to each of the levers 830, 840, 850 so that the working position of the rocker arm 820 is defined by the one of the three levers 830, 840, 850 which is displaced on the largest stroke.

More specifically, as illustrated in the accompanying figures, it is preferably provided two large lateral levers 830, 850 flanking a central lever of shorter length 840.

The rocker arm 820 can bear directly on the heads 676, 686 of the half-shafts 670, 680. However, preferably, there is provided a ring 860 (see figure 41 ) interposed between the rocker arm 820 and the rear face of the heads 676, 686. The ring 860 surrounds the tails 677, 687.

Thus, two independent commands of the half-axes 670, 680 are defined: one which concerns only the half-axis 670 generated by the jack 810, the other which concerns the two half-axes 670, 680 generated by the cylinders 834, 844, 854 via the levers 830, 840, 850, the rocker arm 820 and the ring 860.

We will now describe the general operation of the mandrel with regard to figures 44 and following appended.

Of course, this description is given solely by way of non-limiting example.

The nip of the beginning of a strip to be wound is by bringing the two jaws 612, 614 against each other. This pinching is carried out by the above-mentioned jaw holders 652, 654 themselves driven angularly by the pinions 658, 659, themselves rotated by the axial translation of the two half-shafts 670, 680. This axial translation is caused by the adjustable load of the six springs 690 previously mentioned.

More precisely still, the gripping of the band and the closing of the jaws 612, 614 is carried out according to the illustrated kinematics on the Figures 44A to 44F .

Originally, the jaws 612, 614 are indexed in a position illustrated on the figure 44A symmetrical with respect to the band. The mandrel slide 630 is approached from the web exit from the guide roll 570.

The rollers 532, 534 are activated to advance the strip towards the jaws 512, 514, for example over a distance of the order of 40 mm, as illustrated in FIG. figure 44B .

As illustrated on the figure 44C the jaws 612, 614 are brought back into a parallel position by retracting the rod of the cylinder 810. It will be noted that preferably the angular position of the mandrel remains identical during the two stages of the Figures 44A and 44B , but on the other hand that the mandrel is angularly recalibrated to go to the step illustrated on the figure 44C . By way of example, the angular position may be 348 °, with respect to an arbitrary referential, for the Figures 44A and 44B and 351 ° for the figure 44C .

As illustrated on Figures 44D , 44E and 44F the jaws 612, 614 are then progressively brought together by successively retracting the rods of the jacks 844, 854 and 834. Here again, a successive angular registration is preferably carried out in order to maintain the interface plane of the jaws 612, 614 in an optimal position . In relation to the aforementioned referential, the position of the figure 44D can be at 356 °, that of the figure 44E at 368 ° and that of the figure 44F at 0 °.

The mandrel is then ready for winding in the position illustrated on the figure 45 after translation of the slide 630 away from the guide roller 570.

The rotation of the mandrel can then be carried out according to the concept of speed regulation previously described.

During this winding illustrated on figures 46 , preferably the upstream rollers 532, 534 are placed in brake function for retaining and ensuring web tension during winding.

The rotation of the mandrel is continuous until the first fraction of the last turn of the element illustrated on the figure 47A .

During the winding and rotation of the mandrel, as illustrated in the figures 46 , the pressurizing roll 620 comes into action when the mandrel is in the 58 ° position and thus the presser can come into contact with the winding up to the symmetrical position of the 58 ° position relative to the axis horizontal, then during 64 °, after which it emerges to start in the same way the next half turn.

During winding the jaws 612, 614 remain in the pinched position until the end of the element. In this position, the set of two jaws 612, 614 constitute the section in fusion with the extended axis.

The figure 47A illustrates the position of the pressure roller 620 on the mandrel 610 at the end of the last complete winding revolution, before the pressure roller 620 moves away from the winding.

The last trick illustrated on figures 47 preferably begins with a first step which corresponds to a stop maintained in position of the mandrel 610 and nip rollers 532, 534, stretched strip. Preferably, in this position, the pressure roller 620 is placed in a 58 ° down position in contact with the winding as shown in FIG. figure 47B .

Then the retractable roller 580 is lowered by activation of the jack 586, as seen in the comparative examination of the Figures 47B, 47C and 47D . In the position illustrated on the figure 47D the retractable roller 580 blocks the wound sheet on the mandrel 610. The heat sealing bar 562 is activated to blow hot air to raise the temperature of the end end of the winding to allow subsequent bonding.

Preferably, the blowing of hot air is operated for a predetermined time. At the step illustrated on the figure 47E , the cutting blade 552 is moved by the jack 556 to cut the end of the winding as seen on the figure 47F . The blade 552 is then retracted.

Then the rotation of the mandrel 610 is restarted, the roll 580 remaining in support.

The rotation of the mandrel 610, roll 580 in support is continued to a given angular address, for example 9 °, as illustrated in FIG. figure 48 as a result, the pressure roller 580 is raised.

Preferably, the rotation of the mandrel is continued for one complete revolution so that the satellite roll 620 continues its crushing work on the last turn wound until docking at a reference angle 356 °. The mandrel is then in the position shown on the figure 49 . Preferably, a succession of cycles of opening / closing of the jaws 612, 614 is carried out to take off the first turn of the winding with respect to the outer surface of the mandrel, in order to facilitate the subsequent extraction of the winding. This last step is schematized on the figure 50 .

The relative displacement of the two jaws 612, 614 during these alternating cycles of opening / closing is operated by axial displacement of the two half-shafts 670, 680, thanks to the control of the cylinders 834, 854. The displacement of the half shafts 670, 680 towards the mandrel 610 causes the rotation of the pinions 658, 659 and jaw holders 652, 654, and thus the jaws 612, 614 themselves.

We have shown on Figures 51A , 52A and 53A , the jaw holder positions 652, 654, the jaws 612, 614, the rocker arm 620 and the levers 830, 840 and 850 in the rest position. This position, in which the two jaws 612 and 614 are contiguous, is that used during the rotation of the mandrel for winding the band.

Preferably, as indicated above, the axial sliding of the half-shafts 670, 680 is carried out according to four particular additional positions of work respectively corresponding to the positions illustrated in FIGS. figures 51 , 52 and 53 with the indices B, C, D and E respectively.

Each of these four additional positions is independently adjustable thanks to the four cylinders previously described 810, 834, 844 and 854.

The pneumatic energy makes it possible to control the thrust force of the jacks and thus to protect the mechanics involved in the kinematics of the jaws.

• la position illustrée sur les figures 51B, 52B et 53B est utilisée pour décoller la spire interne de l'enroulement par rapport à la surface extérieure du mandrin 610 (dans cette position, les faces internes des deux mors 612 et 614 sont parallèles et placées dans leur écartement maximal),
• la position illustrée sur les figures 51C, 52C et 53C est utilisée pour opérer le retrait de l'enroulement (dans cette position les faces internes des deux mors 612 et 614 sont parallèles et écartées pour permettre le retrait du début de bande, cependant l'écartement est inférieur à celui des figures d'indice B pour éviter un collage de la spire interne de l'enroulement sur la surface externe du mandrin 610),
• la position illustrée sur les figures 51D, 52D et 53D est une étape intermédiaire préparatoire à l'ouverture pour la saisie du début de bande en vue d'un enroulement (les faces internes des mors 612 et 614 sont écartées et les mors sont inclinées par rapport à la position occupée sur les figures précédentes), et
• la position illustrée sur les figures 51E, 52E et 53E est utilisée pour la saisie du début de bande (les surfaces internes des mors 612 et 614 sont écartées et obliques entre elles ; elles forment un dièdre concave en direction du rouleau d'alimentation 570).

More precisely :

• the position illustrated on the Figures 51B , 52B and 53B is used to detach the inner turn of the winding from the outer surface of the mandrel 610 (in this position, the inner faces of the two jaws 612 and 614 are parallel and placed in their maximum spacing),
• the position illustrated on the Figures 51C , 52C and 53C is used to operate the withdrawal of the winding (in this position the inner faces of the two jaws 612 and 614 are parallel and spaced apart to allow the removal of the beginning of the strip, however the spacing is smaller than that of the figures of index B to prevent sticking of the inner turn of the winding on the outer surface of the mandrel 610),
• the position illustrated on the Figures 51D , 52D and 53D is an intermediate step preparatory to the opening for entry of the beginning of the tape in view of a winding (the inner faces of the jaws 612 and 614 are spaced apart and the jaws are inclined with respect to the position occupied in the preceding figures), and
• the position illustrated on the figures 51E , 52E and 53E is used to enter the beginning of the band (the inner surfaces of the jaws 612 and 614 are spaced apart and oblique to one another and form a concave dihedron in the direction of the feed roller 570).

The position illustrated on the Figures 51B , 52B , 53B allows a strong retraction of the major axis of the jaws 612, 614. It thus allows to give "belly" to the wound element. It is given by the action of the cylinder 854 which pushes the ring 860, for example over a distance of 7.5 mm, causing an angular movement of the jaws and jaw holders each at a given angle, for example 7.5 °.

The position illustrated on the Figures 51C , 52C and 53C , is obtained by activation of the cylinder 834, having for example an axial stroke of 4.5mm to cause an angular movement of the jaws and jaw holder controlled, for example each 4.5 °.

During the aforementioned sequence illustrated on the figure 50 , we can go several times from the position shown on the Figures 51B , 52B , 53B in the position illustrated on the Figures 51C , 52C , 53C , successively, to create a break in adhesion between the jaws 612, 614 and the first wound coil.

The final position of the chuck 610 is preferably that illustrated on the Figures 51C , 52C and 53C , Waiting situation extraction of the wound element, thanks to the robot 700.

It will be noted, however, that before. to extract the wound element, preferably the mandrel operates an angular correction to compensate for the angular offset caused by the opening of the jaws. Indeed, preferably, the robot 700 is adapted to take the wound element in a horizontal position, which requires that the tips of the spindles constituting the mandrel are located in this horizontal position.

After extraction of the element, the mandrel is of course prepared and moved to its full asymmetrical opening position of the jaws for the introduction of the beginning of the band of the new element to be wound.

This preparation sequence is operated by passing successively through the positions illustrated on the Figures 51D , 52D , 53D then 51E, 52E, 53E.

The position illustrated on the Figures 51D , 52D and 53D is due to the action of the cylinder 844 which urges the thrust ring 860 to a typical length of the order of 13mm and therefore causes a typical rotation of the order of 13 ° on each jaw 612, 614.

Then we move to the position illustrated on the figures 51E , 52E and 53E by activating the cylinder 810, the cylinder 834 remaining itself activated. The maximum opening of the jaws 612, 614 is thus obtained as illustrated in FIG. figure 52E . This position must be indexed by checking the orientation of the mandrel, for example at the position 348 °, so that the jaw formed by the two jaws 612, 614 is symmetrical with respect to the horizontal axis to come take the band of symmetric way, as originally indicated with regard to the figure 44A .

The relative movement of the aforementioned means can be controlled by any appropriate means.

We illustrated on the figure 34 a sensor 632 carried by the carriage 630 facing the path of movement of a sensing element 663 carried by the mandrel body 660 to control the rotational movement of the mandrel body 660 relative to the drawer 630.

The means ensuring the relative displacement control jaws 612, 614 through an opening in the vertical wall of the frame delimiting the two aforementioned compartments, to allow translation displacement with the carriage 630.

Naturally, the present invention is not limited to the particular embodiments which have just been described, but extends to any variant within its spirit.

Although the mechanical depelliculation by blade, previously described, is preferred because it avoids the introduction of chemical into the environment of the process, alternatively, it is possible to de-cellulite the complexes using an injected jet of solvent at the interface between the outer face of the complex and the film in question.

The device according to the invention may also comprise de-coating means comprising means for applying an air jet, preferably cold, to the region of divergence between the film and the assembly from which it is deflected.

Similarly hot air furnaces may be replaced by heated rollers.

An embodiment has been illustrated in the appended figures and described above in which the final 6-layer complex is operated by in situ stacking of three base complexes respectively at 1, 2 and 3 layers, initially separated and prerealized. Alternatively, however, it is conceivable in the context of the present invention to feed the mandrel 610 with the aid of such a 6-layer complex pre-realized on a suitable machine. In this case, the interruption of the lithium anode must preferably be integrated in this complex. According to yet another variant, in the context of the present invention, the various base complexes could be made in situ on the device of the invention, from monolayer films.

The different mechanical cutting means previously described may be replaced by any equivalent means, for example based on laser.

The mandrel 610 can itself be the subject of many variants.

We illustrated on the figure 54 , an alternative embodiment in which the mandrel is formed of a single piece. This piece 610 has a spindle cross section similar to that defined by the combination of the two jaws 612, 614 previously described. However, the examination of the figure 54 , the presence, in the aforementioned part, a rectilinear slot 619 for receiving the end of the strip to be wound.

Typically this slot 619 extends over only a portion of the length of the mandrel 610, parallel to the tapered edges thereof and substantially midway between these ridges.

Any suitable means may be associated with such a mandrel to successively open the slot 619 to allow the engagement of a strip end, then allow the closing of the slot to allow the winding and / or "aerate" the winding .

By way of nonlimiting example, bringing the two parts of the mandrel located on either side of the slot 619, to ventilate the wound element and allow its extraction, can be operated by the robot 700 itself.

We have shown on Figures 55a and 55b , another embodiment of mandrel.

According to this variant, the mandrel is formed of several parts capable of relative displacement parallel to the axis of rotation 611 and forming in combination, in the working position illustrated on the figure 55a , an envelope identical to the aforementioned mandrel having a cross-section in the form of a spindle.

According to the particular nonlimiting embodiment illustrated on the figures 55 , the mandrel is thus formed of three pieces: a central piece 1610 framed by two side pieces 1612, 1614. Alternatively, the mandrel could be formed of only two such pieces. Moreover, it will be noted that each of the parts 1610, 1612, 1614 has a "radial" dimension, viewed transversely to the axis of rotation 611, which is progressive when moving along its length, parallel to this axis. More precisely, the radial dimension of the central part 1610 moves in the opposite direction to that of the lateral parts 1612 and 1614.

Thus, those skilled in the art will understand in the comparative examination of Figures 55A and 55B , that when a relative movement is made between the parts 1610 on the one hand, and 1612, 1614 on the other hand, parallel to the axis 611, by any appropriate means, the size or major axis of the section of the mandrel, varies.

The mandrel shown on the Figures 55A and 55B has another feature: at least one of the elements, for example the central element 1610, has a cavity which opens on its external surfaces via a grid of orifices 1613. Thus by connecting the internal cavity of the piece 1610 to a vacuum means, can be pressed the end of the strip to wind on the mandrel 610 by suction.

We have shown on figures 55 means for guiding the parts 1610, 1612, 1614 between them of the dovetail type. Of course, any equivalent guide means could be retained.

We have illustrated on figures 56 , another variant embodiment according to which the mandrel is also formed by the combination of several parts, for example a central part 1610 and two lateral parts 1612, 1614 capable of relative displacement according to at least one component parallel to the axis of rotation 610 More precisely according to the embodiment shown on the figures 56 , the side parts 1612, 1614 are articulated on a common support 1615 and the central part 1610, movable relative to this common support, parallel to the axis of rotation 611, plays by wedge effect to change the spacing between them this.

We have schematised on the figure 57 , an alternative embodiment according to which, while retaining the same chuck section as that described above, with particular reference to the figure 2 , the control of relative movement of the jaws 612, 614 is simplified by keeping only movements in translation of the jaws 612, 614 parallel to each other in a direction of translation that is not parallel to the interface plane 613, that is to say according to a trajectory referenced T on the figure 57 oblique with respect to the interface plane 613 of the jaws.

Of course, the invention is not limited to the precise spindle shape of the mandrel illustrated on the figure 2 .

For example, we have illustrated on the figure 58 , a mandrel formed by combining two jaws 612, 614 defining in combination a mandrel of generally rectangular cross section with rounded edges.

We have shown on figures 55 a chuck whose cross section is modified by relative movement of parts 1610, 1612 and 1614 parallel to the axis of rotation 611.

It is also conceivable to modify the cross section of the mandrel 610, in particular the major axis of the straight section of the mandrel, by moving two lateral pieces 1612, 1614 radially towards and away from the axis 611 and a central piece. 1610.

The various chuck variants previously described comprise parts that define a continuous winding surface.

Alternatively, it is conceivable to realize the mandrel in the form of two separate parts 1612 and 1614 embodying the edges 615, 616, the central portion of the mandrel remaining recessed as shown in FIG. figure 59 . Preferably, these parts 1612, 1614 are controlled on a radial displacement control relative to the axis of rotation 611 to facilitate the release of the wound element by reducing the major axis of the mandrel.

Claims (29)

1. A device for making electrical energy storage assemblies comprising a mandrel (610) adapted to wind superimposed films as a multilayer assembly, characterised in that the mandrel (610) is formed by two complementary jaws (612, 614), the cross-section of the mandrel (610) having a spindle-shaped general cross-section and in that it comprises means (670, 680, 800) able to modify on request the cross-section of the mandrel (610), the modification of the cross-section of the mandrel (610) comprising reducing the length of the major axis of the cross-section of the mandrel (610), the means (670, 680, 800) being designed to provide on request a relative displacement of both jaws (612, 614) making up the mandrel (610), with respect to each other, along at least one component transverse to the axis of rotation (611) of the mandrel (610).
2. The device according to claim 1, characterised in that a modification of cross-section of the mandrel (610) is intended for pinching one end of the films to be wound, causing the winding.
3. The device according to one of claims 1 and 2, characterised in that a modification of cross-section of the mandrel (610) is intended for causing a general loosening of the winding, that is creating some clearance between the winding and the outer surface of the mandrel (610), to facilitate the extraction of the winding.
4. The device according to one of claims 1 to 3, characterised in that each jaw (612, 614) is attached to a respective jaw holder (652, 654), itself rotatably mounted, on a mandrel body (660), about respective axes (656, 657) parallel and off-centred to the axis of rotation (611) of the mandrel (610).
5. The device according to claim 4, characterised in that each jaw holder (652, 654) is provided with a helical cut pinion (658, 659) and associated with a drive element (670, 680) translationally guided relative to the body (660) and itself provided with a helical pinion (672, 682) respectively complementary and engaged with one of the pinions (658, 659) provided on the jaw holders.
6. The device according to claim 5, characterised in that it comprises two juxtaposed drive elements (670, 680) individually translationally guided on a spindle forming sheath (662) providing rotational guiding of the mandrel (610) about its axis (611).
7. The device according to one of claims 5 and 7, characterised in that each drive element (670, 680) comprises a segment (674, 684) having a non-circular revolution cross-section arranged in a segment having a cross-section complementary to the body (660), providing anti-rotation connection of each drive element (670, 680) with respect to the body (660).
8. The device according to one of claims 5 to 7, characterised in that each drive element (670, 680) comprises a half-crown shaped widened head (676, 686).
9. The device according to one of claims 5 to 8, characterised in that each drive element (670, 680) is selectively biased in several chosen positions by mechanical means (800).
10. The device according to one of claims 5 to 9, characterised in that it comprises a cylinder (810) adapted to bias one of the drive elements (670, 680).
11. The device according to one of claims 5 to 10, characterised in that it comprises control means (830, 840, 850, 834, 844, 854) adapted to bias both drive elements (670, 680) on an identical stroke.
12. The device according to claim 11, characterised in that the control means comprise a rotatably mounted rocker arm (820), hinged levers (830, 840, 850) adapted to bias the rocker arm (820) and cylinders (834, 844, 854) adapted to bias the levers (830, 840, 850).
13. The device according to claim 12, characterised in that it comprises three levers (830, 840, 850) and three associated cylinders (834, 844, 854) .
14. The device according to one of claims 12 and 13, characterised in that the rocker arm (820) presses against a ring (860) sandwiched between the rocker arm (820) and widened heads (676, 686) provided on the drive elements (670, 680).
15. The device according to one of claims 1 to 14, characterised in that it comprises mechanical means (800) adapted to sequentially drive either a relative tilt between both jaws (612, 614) forming the mandrel, to provide opening and closing upon gripping and releasing the winding, or a relative displacement of both jaws (612, 614) parallel to each other, in order to modify the length of the major axis and the minor axis of the mandrel during a final sequence of extraction of the winding.
16. The device according to one of claims 1 to 15, characterised in that it comprises means able to make an angular reset of the mandrel with respect to a reference frame, during at least some of the modifications of cross-section of the mandrel (610).
17. The device according to one of claims 1 to 16, characterised in that it comprises control means (670, 680, 800) adapted to selectively define five predetermined states of cross-section of the mandrel (610).
18. The device according to one of claims 1 to 17, characterised in that it comprises control means (670, 680, 800) adapted to determine at least four relative positions of both jaws (612, 614):

    . a position in which the jaws (612, 614) are adjoined, for winding the films,

    . a position in which the inner faces of both jaws (612, 614) are parallel and placed in their maximum gap to move the inner turn of the winding away from the outer surface of the mandrel (610),

    . a position in which the inner faces of both jaws (612, 614) are parallel and spaced apart by a value lower than the previous position, to cancel the pinching of the leading band during an extraction of the wound element,

    . a position in which the inner surfaces of the jaws (612, 614) are spaced apart and oblique to each other.
19. The device according to one of claims 1 to 18, characterised in that it comprises elastic means (690) able to make a controlled tightening strain on the jaws (612, 614).
20. The device according to one of claims 1 to 19, characterised in that the mandrel (610) has a cavity adapted to be connected to a depression means and which opens onto at least one outer surface.
21. The device according to one of claims 1 to 20, characterised in that the mandrel (610) is placed on a drawer (630) translationally movable with respect to the machine frame.
22. The device according to claim 21, characterised in that it comprises a mandrel body (660) rotatably mounted onto the drawer (630).
23. The device according to claim 22, characterised in that it comprises two jaw holders (652, 654) rotatably mounted on the body (660) about axes (656, 657) off-centred to the axis of rotation (611) thereof.
24. The device according to claim 23, characterised in that it further comprises two half-axes (670, 680) translationally mounted in the body (660) for controlling the jaw holders (652, 654).
25. The device according to one of claims 21 to 24, characterised in that it further comprises a press roll (620) mounted through a rotatable arm (624) on a carriage (693), itself translationally movable with respect to the drawer (630).
26. The device according to claim 25, characterised in that the rotatable arm (624) is driven through a constant speed universal joint (696).
27. The device according to one of claims 25 and 26, characterised in that the press roll (620) is equipped with a swinging system for allowing self-alignment against the turns during winding.
28. The device according to one of claims 25 to 27, characterised in that the rotatable arm (624) is rotatably driven at a speed twice as fast as that of the mandrel (610).
29. A method for making electrical energy storage assemblies by winding superimposed films, on a mandrel (610), as a multilayer assembly, characterised in that it comprises at least one step of modifying on request the cross-section of the mandrel (610), having a spindle shaped general cross-section, by reducing the length of the major axis of the cross-section of the mandrel (610), the modification being made by relatively displacing both jaws (612, 614) making up the mandrel (610), with respect to each other, along at least one component transverse to the axis of rotation (611) of the mandrel (610).

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